EP3488127B1 - Einteiliger ölabstreifring - Google Patents

Einteiliger ölabstreifring Download PDF

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Publication number
EP3488127B1
EP3488127B1 EP17725940.5A EP17725940A EP3488127B1 EP 3488127 B1 EP3488127 B1 EP 3488127B1 EP 17725940 A EP17725940 A EP 17725940A EP 3488127 B1 EP3488127 B1 EP 3488127B1
Authority
EP
European Patent Office
Prior art keywords
ring
joint
oil scraper
depth
piece oil
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP17725940.5A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3488127A1 (de
Inventor
Richard Mittler
Fabian RUCH
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Federal Mogul Burscheid GmbH
Original Assignee
Federal Mogul Burscheid GmbH
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Publication date
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Publication of EP3488127A1 publication Critical patent/EP3488127A1/de
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J9/00—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction
    • F16J9/12—Details
    • F16J9/20—Rings with special cross-section; Oil-scraping rings
    • F16J9/206—One-piece oil-scraping rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J9/00—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction
    • F16J9/12—Details
    • F16J9/20—Rings with special cross-section; Oil-scraping rings

Definitions

  • the present invention relates to piston rings, in particular a one-piece oil control ring.
  • One of the main problems in four-stroke engines is to control and seal the piston ring-piston system from and with oil present in the crankcase; piston rings are used for this purpose, which are intended to seal the combustion chamber as well as possible from the crankcase oil.
  • a certain amount of oil in the system is necessary to ensure the functionality of the piston ring system in terms of friction and the sealing of gas from the combustion chamber.
  • this defined amount of oil should be kept as small as possible without, on the other hand, preventing the hydrodynamic lubricating film on the piston ring running surfaces.
  • the oil control ring must achieve control for a perfect balance between oil emissions, functionality and wear resistance.
  • Oil control rings hereinafter also referred to as oil rings, are currently mostly used as two- or three-part designs in LVD, LVP HD motors.
  • a ring carrier is designed with an internal spring.
  • two webs Arranged on the running surface of the piston ring are two webs which strip off excess oil from the cylinder wall, openings between the webs, in the form of, for example, bores or slots, which guide excess oil from the outside to the inside of the piston ring.
  • the webs With regard to their height and depth and their arrangement on the tread, the webs are usually designed symmetrically.
  • the internal spring creates the necessary forces to press the outer running surface of the piston ring, ie the webs arranged on the running surface, against the cylinder wall.
  • a one-piece oil control ring according to the prior art is known from US 1,832,795 .
  • a one-piece oil scraper ring which has an annular body with a constant radial thickness in the circumferential direction, two webs being axially spaced apart from one another in the circumferential direction by an outer groove, and openings being arranged radially from the bottom the outer groove runs to the inside of the ring body, two inner grooves are arranged on the inside of the ring body, which run in the circumferential direction and where in one (respective) area of each butt end one of the inner grooves begins, and the cross-sectional area of the inner grooves from the ring joint towards the ring back decreases, the depth of the inner grooves decreasing from the ring joint in the direction of the ring back, the openings being arranged only within an angular range from 0 to 135 ° and from 225 ° to 360 ° measured from the ring joint.
  • the openings are arranged within an angular range from 0 ° to 90 ° and from 270 ° to 360 ° measured from the ring joint.
  • the depth of the inner grooves in an angular range measured from the ring joint is 135 ° to 225 °, preferably in an angular range from 165 ° to 195 °, more preferably in a narrow angular range which is essentially only that Includes 180 ° angle, zero.
  • the depth of the internal grooves decreases proportionally with the angle measured from the ring joint.
  • the start of the inner grooves is spaced from the respective butt end.
  • the axial height of the inner grooves on the inside of the ring is smaller than the total axial height of the ring.
  • the axial height of the inner grooves on the inside of the ring decreases from the ring joint in the direction of the ring back.
  • the maximum depth of the internal grooves is in a range from 25% to 100%, preferably from 50% to 100%, more preferably from 75% to 100%, of the axial height of the oil control ring.
  • the depth of the outer groove decreases from the two butt ends in the direction of the ring back.
  • the depth of the outer groove is in an angular range from 135 ° to 225 ° measured from the ring joint, preferably in an angular range from 165 ° to 195 °, more preferably in a narrow angular range which essentially only includes the angle 180 ° , constant.
  • the depth of the external groove decreases proportionally with the angle measured from the ring joint.
  • the upper and the lower half of the ring body are symmetrical to one another.
  • the usual designation is followed that axially relates to the corresponding direction of the piston, that is to say the direction of the reciprocating movement thereof, or to the corresponding axis of the piston-cylinder.
  • the ring axis is the axis running through the center of the ring in the axial direction, which in the installed state coincides with the central axis of the piston.
  • a radial direction is accordingly a direction which, parallel to the ring plane, runs at right angles to the ring axis or at right angles to it.
  • An axial cut is a cut whose cutting plane contains the ring axis.
  • the oil ring described here is characterized by a design without a spring, the necessary tangential force (contact pressure) being generated by an appropriate design.
  • the spread and wall thickness of the ring are chosen so that the surface pressure corresponds to today's two- or three-part oil scraper rings.
  • the cross section of the ring body is varied accordingly by internal grooves in the direction of rotation. Since the annular body has a constant radial thickness and a constant axial height in the circumferential direction, the cross-sectional area of the internal grooves is varied in the circumferential direction for this purpose, and the external one can also be used Groove of the oil control ring can be varied.
  • a first exemplary embodiment of the oil scraper ring according to the invention is shown, which produces the variation of the cross-sectional area by changing the depth of internal grooves.
  • the oil scraper ring comprises an annular body 1 which has a radial thickness D and height which is constant in the circumferential direction.
  • the thickness here is the radial extension of the ring body in an axial section, the radially outermost or innermost lines / surfaces can thus serve as a reference in the radial direction for determining the radial depth of the grooves.
  • depth at an angular position in the circumferential direction is understood to mean the radial distance from a radially outermost point of the groove to a radially innermost point of the surface of the piston ring inside in an axial section at this angular position, or in other words the maximum extent of the groove in radial direction in an axial section at this angular position.
  • the two inner grooves 5 each have their greatest depth in an area near the two butt ends.
  • the inner grooves can be designed in this way if necessary that they only start at a distance from the butt ends, so a thin web (1 mm to a few mm for a ring with, for example, 80 mm or 100 mm diameter) remains at the butt ends.
  • the depth Ti of the inner grooves 5 decreases in the direction of the ring back, and there is no longer a groove in the region of the ring back. As the depth Ti of the internal grooves decreases, their cross-sectional area also decreases.
  • axial sections 5a, 5b, 5c, 5d of one of the inner grooves are sketched for this purpose.
  • the depth Ti of the internal grooves is only shown for section 5d, which corresponds to the angular position d closest to the ring joint.
  • the inner grooves are shown here as parabolic, but other shapes are also conceivable, for example another rounded shape (ellipse, circle), a rectangular groove or a V-shaped groove.
  • the axial height measured at a certain radial distance from the inside of the ring decreases with the depth, which also contributes to the decrease in the cross-sectional area.
  • This effect may also occur with differently shaped grooves; eg with a V-shape, but not with a rectangular shape.
  • the depth Ti of the internal grooves 5 decreases from the ring joint in the direction of the ring back. This decrease is preferably carried out essentially in a proportional manner with the angle measured from the ring joint. The angle is selected so that the ring joint is at 0 °, the ring back at 180 °. The groove is no longer present on the ring back itself, so to speak the depth Ti of the inner grooves 5 here is zero. On the ring back (the in Fig. 1 the angular position a corresponds), the inside of the ring is thus formed in a certain angular range without a groove.
  • This angular range can be 135 ° to 225 °, preferably 165 ° to 195 °, further preferred is only a narrow angular range, maximum ⁇ 5 °, which essentially only includes the angle 180 °, without a groove.
  • the depth Ti of the inner grooves 5 in the area near the ring joint in which the grooves begin should be in a range from 25% to 100%, preferably in one Range of 50% to 100%, more preferably in a range of 75% to 100%, the axial height of the oil control ring.
  • the maximum depth of the internal grooves should not exceed 100% of the axial height of the oil ring, since otherwise the remaining radial ring thickness becomes too small and the risk of breakage increases.
  • the openings 3 for the oil flow are arranged only in the areas of the smaller wall thicknesses.
  • the angular range is from -135 ° to + 135 °, i.e. 225 ° to 360 ° and 0 ° to 135 °, preferably from -90 ° to + 90 °, i.e. 270 ° to 360 ° and 0 ° to 90 °.
  • the edge of the groove does not necessarily have to meet with the upper and lower inner ring edges, as shown in the figure.
  • the surface of the inside of the ring can, for example, have upper and lower regions that are parallel to the ring axis, that is to say have no groove, while the inner groove is only in an intermediate central region. If the axial height of the inner grooves at an angular position in the circumferential direction is defined as the maximum extent of the inner grooves in the axial direction in an axial section at this angular position, then this axial height of the inner grooves is at least within a certain angular range less than the total height of the ring.
  • the axial height of the inner grooves preferably decreases starting from the ring joint in the direction of the ring back, so that the cross-sectional areas of the inner grooves also decrease in the direction of the ring back if the depths of the inner grooves do not increase.
  • the axial height of the inner grooves in the positions of the is also conceivable Reduce openings to compensate for the weakening of the ring body caused by openings at these points.
  • the upper and the lower half of the ring are preferably symmetrical to one another, i.e. mirror-symmetrical with respect to a level at half the ring height, so that no ring twist occurs when installing the oil scraper ring and the two webs 2 rest against the cylinder wall with a uniform surface pressure both in the direction of rotation and in relation to one another.
  • the internal grooves 5 themselves are designed symmetrically, this is achieved by arranging these grooves centrally with respect to the axial height of the ring body 1.
  • the running surface and the openings 3 should also be designed accordingly in order to avoid twisting of the ring under tension.
  • the depth Ta (again shown as representative only for 4d) of the outer groove 4 also varies. This is on the left-hand side of FIG Figure 2A in axial sections 4a, 4b, 4c, 4d, which correspond to the angular positions a, b, c, d on the right side of the figure.
  • the outer groove 4 has its greatest depth at the two ends of the joint and its depth Ta decreases from the ring joint in the circumferential direction in the direction of the ring back, with which the cross section varies.
  • the groove walls in a radially outer region preferably run as perpendicularly as possible to the ring axis.
  • the bottom of the outer groove 4 can - similar to the bottom of the inner grooves 5 - have a rounded (for example parabolic as in the figures) or a polygonal shape.
  • the decrease in the depth Ta of the outer groove 4 in the direction of the ring back can take place in a manner proportional to the angle measured from the ring joint.
  • the outer groove 4 can have a constant depth Ta, which should be greater than zero, since otherwise there would no longer be two wiper webs on the ring back, which considerably restricted the function of the oil ring.
  • This is preferably from the ring joint measured angular range with constant external groove depth Ta between 135 ° and 225 °, more preferably between 165 ° and 195 °, most preferably in a narrow range which essentially only includes the angle 180 °.
  • This design of the outer groove 4 ensures a specific oil flow on the outside of the ring in the direction of the openings 3, which, as already explained above, are preferably located in an area with a smaller ring thickness, that is to say in an area near the ring joint.
  • the volumes provided by the cross-sectional area of the inner grooves 5 and the additional depth of the outer groove 4 can also absorb oil and improve the control of the oil flow.
  • the volume is increased compared to the volume at the ring back, an oil flow in the direction of the ring joint, in the vicinity of which the openings are made, is guaranteed.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
EP17725940.5A 2016-07-25 2017-05-23 Einteiliger ölabstreifring Active EP3488127B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016113678.6A DE102016113678B4 (de) 2016-07-25 2016-07-25 Einteiliger Ölabstreifring
PCT/EP2017/062345 WO2018019445A1 (de) 2016-07-25 2017-05-23 Einteiliger ölabstreifring

Publications (2)

Publication Number Publication Date
EP3488127A1 EP3488127A1 (de) 2019-05-29
EP3488127B1 true EP3488127B1 (de) 2020-06-17

Family

ID=58772884

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17725940.5A Active EP3488127B1 (de) 2016-07-25 2017-05-23 Einteiliger ölabstreifring

Country Status (10)

Country Link
US (1) US10969014B2 (pt)
EP (1) EP3488127B1 (pt)
JP (1) JP2019523370A (pt)
KR (1) KR20190031248A (pt)
CN (1) CN109312863B (pt)
BR (1) BR112018075153A2 (pt)
DE (1) DE102016113678B4 (pt)
PT (1) PT3488127T (pt)
RU (1) RU2733910C2 (pt)
WO (1) WO2018019445A1 (pt)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015116838B3 (de) * 2015-10-05 2017-02-02 Federal-Mogul Burscheid Gmbh Kolbenring
KR102648295B1 (ko) * 2022-05-18 2024-03-14 한국핵융합에너지연구원 실링용 c 타입 링
CN115306580B (zh) * 2022-08-29 2024-03-01 奇瑞汽车股份有限公司 一种提升发动机油环刮片质量的方法

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US1378894A (en) 1917-11-28 1921-05-24 Edward R Norman Packing-ring
US1327801A (en) * 1918-09-06 1920-01-13 Blache Hans Henrik Scraper-ring for scraping oil from cylinders, piston-rods, or the like
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US1965623A (en) * 1930-02-03 1934-07-10 Wilkening Mfg Co Piston ring
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Also Published As

Publication number Publication date
KR20190031248A (ko) 2019-03-25
BR112018075153A2 (pt) 2019-03-26
WO2018019445A1 (de) 2018-02-01
RU2019101773A (ru) 2020-08-25
US20190154152A1 (en) 2019-05-23
JP2019523370A (ja) 2019-08-22
RU2019101773A3 (pt) 2020-08-25
US10969014B2 (en) 2021-04-06
PT3488127T (pt) 2020-09-10
RU2733910C2 (ru) 2020-10-08
CN109312863A (zh) 2019-02-05
DE102016113678A1 (de) 2018-01-25
CN109312863B (zh) 2021-05-28
DE102016113678B4 (de) 2018-05-09
EP3488127A1 (de) 2019-05-29

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